TW201718176A - Tail stock device for supporting and/or centering a workpiece - Google Patents

Abstract

The invention relates to a tail stock device (10) for supporting a workpiece in a machine tool, for example a grinding machine. The tail stock device (10) comprises a tail stock arm (16) that is pivotally supported about a pivot axis (S), said tail stock arm having arranged on its outer end (16a) a centering tip (12) that is oriented parallel to the pivot axis (S). By means of a pivot drive (30) comprising a first pneumatic cylinder (31), the tail stock arm 16 can be pivoted between a working position (A) and a resting position (R). The movement of the piston (32) of the first pneumatic cylinder (31) is transmitted - via a first coupling arrangement (35) - to the tail stock arm (16). When the tail stock arm (16) is in working position (A), the first coupling arrangement (35) assumes a self-locking position in which a force feedback effect being triggered by a torque that forces the tail stock arm (16) out of working position (A) and into resting position (R) does not or only minimally retroact on the piston (32) of the first pneumatic cylinder (31).

Description

Tailstock device for supporting and/or centering a workpiece

The present invention relates to a tailstock assembly for supporting and/or centering a workpiece. In a processing machine, the tailstock is specifically configured to support the end of a workpiece, the workpiece being preferred relative to the surface of the collet.

A tailstock for a grinder is known, for example, from German Patent No. DE 35 17 802 A1. The tailstock has a lower portion of the tailstock and an upper portion of the tailstock that are interconnected to pivot about a pivot. For pivotal movement, the tailstock contains a pivot drive. Via the pivoting drive, the upper portion of the tailstock carrying the support configuration for the workpiece has the potential to move into or out of the working area of the grinding disc. As such, the sleeve axis of the tailstock extends tangentially relative to the pivot.

The space requirement of this tailstock device is very large. Even if the upper part of the tailstock pivots away from the work area, this part still requires considerable machine space.

In view of this prior art, it is apparent that the object of the present invention is to provide a tailstock device that can be configured and actuated in a simple manner and that makes it possible to achieve space saving.

This object is achieved with a tailstock device having the features described in claim 1 of the patent application.

The tailstock assembly includes a carrier configuration. The carrier configuration is configured to be connectable to a machine tool and to include, for example, suitable mounting components for this purpose. A tailstock arm is disposed on the carrier arrangement. The inner end of the tailstock arm is supported by the carrier arrangement such that the arm is pivotable about a pivot. A support arrangement is included on the outer end opposite the inner end of the tailstock arm. The support arrangement can include a central tip that interacts with a central aperture in front of the workpiece to support and/or center the workpiece.

In addition, a pivoting drive is provided on the carrier arrangement. The pivot drive includes a first pneumatic cylinder and a first coupling configuration. The piston of the first pneumatic cylinder is movably coupled to the inner end of the tailstock arm via the first coupling arrangement. With the pivoting drive, the tailstock arm is movable between an upright working position and a lying rest position, preferably in a range of pivoting angles of up to 90° to 100°. As such, the first coupling configuration is assembled in such a way that it at least reduces or completely eliminates any force feedback by bringing pivot-centered torque whenever the tailstock arm is in the operating position. A self-locking effect caused by the torque shifting the tailstock arm away from its working position in the direction of the idle position.

Therefore, the compressible air of the pneumatic cylinder can be prevented from causing the tailstock to remain in the working position. As such, the stiffness of the configuration is sufficiently high to maintain the tailstock arm in the exact position of the working position. This prevents unintentional pivoting away from the direction of the idle position work location.

It is advantageous if the first coupling arrangement comprises a pivoting lever that is coupled to the inner end of the tailstock arm in a torque-proof manner and that extends from the pivot end of the rod. Additionally, the first coupling arrangement can include a connector rotatably coupled to the rod end with a first hinge. Furthermore, the connector can be rotatably coupled to the actuating element via a second hinge. Next, the actuating element is preferably rigidly coupled to the piston of the first pneumatic cylinder in a longitudinally reciprocable manner of the piston. According to this embodiment, the longitudinal orientation is at right angles to the pivot. As such, the first coupling configuration forms a lever mechanism. Preferably, the actuating element comprises a degree of freedom only in the longitudinal direction. The actuating element is connectable to a piston rod of the first pneumatic cylinder.

As such, it is advantageous if the orientation of the connector is substantially at right angles to the tailstock when the tailstock arm is in the operative position. It should be understood that the phrase "substantially at right angles" means, for example, a right angle corresponding to approximately 90 degrees and may be in the range of 80 to 100 degrees.

Moreover, when the tailstock arm is in the operative position, it is advantageous if the orientation of the connector is substantially at right angles to the actuating element.

Preferably, the connector extends parallel to the tailstock arm when the tailstock arm is in the operative position, or an acute angle of at most 5 degrees or at most 10 degrees or at most 15 degrees.

By the orientation of the connector when the tailstock arm is in the operative position, when a pivot-centered torque is applied to the tailstock arm, it is possible to almost or completely eliminate the force in the direction of the piston of the first pneumatic cylinder. Feedback. If the positioning of the connector is at right angles or nearly a right angle to the longitudinal direction, no or only minimal force can be transmitted to the actuating element by the torque of the tailstock arm, thereby preventing compression of the air in the pneumatic cylinder. result, This configuration has a large stiffness when the tailstock arm is in the working position.

Preferably, the actuating element is movable within only one degree of freedom and is configured to be longitudinally displaceable in the carrier configuration in the exemplary embodiment.

In view of a preferred exemplary embodiment, the tailstock assembly includes a stop disposed in or formed by the carrier configuration. The pivot drive forces the tailstock arm against the stop when the tailstock arm is in the operative position. Preferably, the stop is associated with the inner end of the tailstock arm.

Furthermore, it is preferred if the carrier arrangement comprises a base body designed to be connectable to machine tools. For this purpose, a suitable mounting member may be present on the seat. Preferably, a carriage is movable within the seat in a single degree of freedom. For example, the bracket can be supported by the seat to be slidable. For example, the bracket can be supported to be slidable in a lateral direction at right angles to the longitudinal direction with a guiding arrangement. The guiding arrangement may comprise pre-stretched cross roller guides for guiding play without play. According to this embodiment, the transverse orientation is parallel to the pivot.

Preferably, the tailstock arm extends from the pivot to the outer end at a right angle to the longitudinal direction and a height direction at a right angle to the lateral direction when in the operative position.

The tailstock arm and the pivoting drive can be disposed on the carriage and move with the bracket relative to the base.

In a preferred exemplary embodiment, a linear actuator for moving the carriage is provided, the linear drive including a second pneumatic cylinder and a second coupling configuration. By means of the linear drive it is possible to move or position the carriage relative to the base.

As a result, the linear drive and the pivoting drive can be actuated pneumatically.

The second coupling configuration preferably includes defining a gate path (gate Path) A gate part of a gate. A gate element is configured to move along the gate path. By means of this embodiment of the second coupling arrangement, the reduction of the path of the piston of the second pneumatic cylinder relative to the carriage is easily achieved.

Preferably, the shutter member is fixedly disposed on the base and extends into a slotted gate. In this way, it can be engaged through the bracket by the corresponding groove. The shutter member is supported such that it can slide longitudinally along the bracket. It can be said that the shutter element, the bracket and the seat form a crisscross bracket arrangement.

If the piston of the second pneumatic cylinder is longitudinally movable, preferably, in this case, the shutter member is connectable to the piston of the second pneumatic cylinder so as to be stationary in the longitudinal direction. Preferably, the shutter member is configured to move within only one degree of freedom and, according to this embodiment, is disposed on the bracket or the seat for longitudinal movement. The bracket is supported at a right angle to the longitudinal direction for longitudinal movement on the seat.

In a preferred exemplary embodiment, the second pneumatic cylinder and the shutter member are disposed on the bracket and move laterally with the bracket for the seat.

In particular, the gate path is configured to be inclined for longitudinal direction and inclined for lateral direction. Preferably, the gate path has a constant inclination angle with respect to the longitudinal direction, for example. The angle of inclination is preferably less than 45° to achieve simplification of the path from the second pneumatic cylinder to the carrier. Due to this inclination angle, in addition to the simplification of the path, force transmission from the second pneumatic cylinder can be achieved. It is preferred if the tilt angle is at most 30° or at most 20° or at most 10°. As a result, due to the volume flow of the air, it is possible to achieve extremely excellent carriage motion control without triggering the movement of the carriage.

10‧‧‧Tailstock device

11‧‧‧Support configuration

12‧‧‧ Centering tip

15‧‧‧Carrier configuration

16‧‧‧Tailstock arm

16a‧‧‧The outer end of the tailstock arm 16

16b‧‧‧The inner end of the tailstock arm 16

20‧‧‧ body

21‧‧‧Installation and configuration

22‧‧‧ bracket

23‧‧‧Guide configuration

24‧‧‧ Track Guides

28‧‧‧ shaft

29‧‧‧ pivot bearing body

30‧‧‧ pivot drive

31‧‧‧First air cylinder

32‧‧‧Piston of the first pneumatic cylinder

33‧‧‧ piston rod

34‧‧‧Actuating element

35‧‧‧First coupling configuration

36‧‧‧Actuating components

37‧‧‧Connecting parts

38‧‧‧ pivot rod

39‧‧‧First hinge

40‧‧‧Second hinge

41‧‧‧Guide

42‧‧‧stop block

45‧‧‧Linear drive

46‧‧‧Second air cylinder

47‧‧‧Second coupling configuration

48‧‧‧ piston rod

49‧‧‧gate components

50‧‧‧rails

51‧‧‧ slotted gate

52‧‧‧ gate surface

53‧‧‧slit

54‧‧‧gate components

55‧‧‧Latch

56‧‧‧Sleeve

57‧‧‧ passage opening

60‧‧‧ cover

‧‧‧‧Tilt angle

A‧‧‧Working position

H‧‧‧ Height direction

L‧‧‧ portrait

Q‧‧‧ Landscape

R‧‧‧Inactive location

S‧‧‧ pivot

Advantageous embodiments of the tailstock device can be inferred from the dependent items, the description and the drawings. Hereinafter, a preferred exemplary embodiment of the tailstock device will be explained in detail with reference to the accompanying drawings.

1 is a perspective view of one exemplary embodiment of a tailstock device; FIG. 2 is a perspective view of the exemplary embodiment of FIG. 1 without a cover; and FIG. 3 is a plan view of the tailstock device of FIG. 2 without a cover; Figure 4 is a perspective sectional view of the tailstock device of Figures 1 to 3 taken along line IV-IV of Figure 3; Figure 5 is a schematic embodiment of the tailstock device of Figures 1 to 4 along Figure 3 A cross-sectional partial view of a section line VV drawn therein; and FIG. 6 is a perspective cross-sectional view of the carrier configuration of the exemplary embodiment of the tailstock apparatus of FIG. 1 through FIG.

FIG. 1 is an exemplary embodiment of a tailstock assembly 10. Figure 1 illustrates a complete tailstock assembly 10 for mounting on a machine tool. The tailstock assembly 10 is configured to support and/or center a workpiece, particularly a cylindrical workpiece. To accomplish this, the tailstock assembly 10 includes a support arrangement 11 which, in the exemplary embodiment, has or is formed with a centering tip 12.

The tailstock assembly 10 includes a carrier arrangement 15 on which a tailstock arm 16 is disposed to enable pivoting about a pivot S. In the exemplary embodiment, the tailstock arm 16 is pivotable about 90° about the pivot S between the working position A and the rest position R (Fig. 1). When in the working position A, the tailstock arm 16 extends away from the pivot S in the height direction H until towards the outer end 16a of the tailstock arm 16. The support arrangement 11 or centering tip 12 is disposed on the other end 16a. Tailstock arm The support 16 is supported on the inner end 16b such that it pivots about the pivot S. The inner end 16b is viewed from the direction of the outer end 16a, and the inner end 16b extends beyond the pivot S. In the exemplary embodiment, the pivot S extends in a lateral direction Q that is at right angles to the height direction H.

According to this embodiment, the carrier arrangement 15 comprises a seat 20 that is configured to be detachably coupled to a machine tool and, for example, a machine tool. To accomplish this, a mounting configuration 21 is provided on the body 20. The bracket 22 is disposed on the base 15 in such a manner that the bracket can slide linearly in the lateral direction. A guiding arrangement 23 for guiding the bracket 22 can be seen in FIGS. 4 and 6. The guiding arrangement 23 includes two track guides 24 that are configured to be spaced apart in a longitudinal direction L that is at right angles to the lateral direction Q and the height direction H. The track guides 24 are assembled to guide the brackets 22 on the seat 20 without play and are formed, for example, by pre-stretched cross roller guides.

The shaft 28 is rotatably supported on the bracket 22 of the carrier arrangement 15 along a pivot S. That is, according to this embodiment, the shaft 28 is rotatably supported by the pivot bearings of the pivot bearing body 29 by the two bearing points spaced apart along the pivot. Both of the pivot bearing bodies 29 are mounted to the bracket 22.

The pivot drive 30 is configured to pivot the tailstock arm 16. The pivot drive 30 includes a first pneumatic cylinder 31 that is assembled into a double-acting cylinder. The piston 32 (Fig. 4) of the first pneumatic cylinder 31 hydrodynamically divides the cylinder chamber into two working chambers. The piston 32 is connected to the piston rod 33 of the first pneumatic cylinder 31. The piston rod 33 is protruded from the cylinder housing. The piston 32 of the first pneumatic cylinder 31 and the piston rod 33 are supported by the bracket 22 so as to be movable in the longitudinal direction L.

The piston rod 33 belongs to a first coupling arrangement 35 with which the piston 32 is movably coupled to the tailstock arm 16. In particular, the first coupling configuration 35 can be seen in FIG. The actuating element 36 is coupled to the piston rod 33 of the first pneumatic cylinder 31 in such a way that the actuating element 36 and the piston rod 33 are not movable relative to each other in the longitudinal direction L. On the opposite side of the piston rod 33, the actuating element 36 is connected The member 37 is coupled to the pivot rod 38. The pivot rod 38 is pivotable about a pivot S and extends from the pivot S toward the rod end. A first hinge 39 is provided on the rod end, and the connecting member 37 is rotatably coupled to the pivot rod 38. The second hinge 40 rotatably couples the actuating element 36 to the connector 37. The two hinge axes of the hinges 39, 40 are oriented parallel to the pivot S. For example, a chain link can be used as the connector 37.

Preferably, the actuating element 36 can only move in one degree of freedom in the longitudinal direction L. In the exemplary embodiment, the actuating element is configured to be at least partially in the guiding recess 41 of the bracket 22 and can be slidably supported in this position.

The pivoting lever 38 is coupled to the tailstock arm 16 in a torque-resistant manner, such as by a shaft 28. The pivot rod 38 can be rigidly disposed on the shaft 28 or be an integral component of the shaft 28. The inner end 16b of the tailstock arm 16 is seated on the shaft 28 in a torque resistant manner and rotates about the pivot S with the shaft 28.

FIG. 4 illustrates the working position A of the tailstock arm 16. The piston rod 33 is removed from the housing of the first pneumatic cylinder 31. The connecting member 37 extends approximately in the height direction H between the pivoting lever 38 and the actuating member 36. In this way, the connector can have an acute angle of 10° to 15° with respect to the height direction H. As a result, when the tailstock arm 16 is in the operating position A and the tailstock arm 16 has the torque to move away from the working position A in the idle position R direction, the connecting member 37 does not apply force or only the minimum force in the longitudinal direction L. A piston applied to the first pneumatic cylinder 31. As a result, the first coupling arrangement 35 exhibits a self-locking feature at the working position A of the tailstock arm 16. As a result, the tailstock arm 16 must not be supported by the aerodynamic force of the first pneumatic cylinder 31 when in the working position A. Due to the compressibility of the air, it is not possible to achieve the exact positioning of the tailstock arm 16 to support the configuration 11 or the centering tip 12.

Depending on which working chamber the compressed air is applied to the first pneumatic cylinder 31, the tailstock arm 16 will remain in the working position A or the idle position R or in both positions. Set A and R to pivot.

When in the working position A, the tailstock arm 16 is in contact with the stop block 42. The stop 42 defines the working position A. In the exemplary embodiment, it is associated with the inner end 16b of the tailstock arm 16. The stop block 42 limits the pivotal movement of the tailstock arm 16 from the rest position R into the working position A while it allows for unimpeded pivotal movement in the reverse direction. As a result, the stop block 42 prevents the undesired pivotal movement of the tailstock arm 16 about the pivot axis S from the working position A in the rotational direction and the aforementioned self-locking effect of the first coupling arrangement 35 into the opposite rotational direction.

The first pneumatic cylinder 31 and the first coupling arrangement 35 are disposed on the bracket 22 together with the tailstock arm 16 and are movable relative to the base 20 in the lateral direction Q together with the bracket 22.

In order to move the carriage 22 along the seat 20 mountable on the machine tool, a linear drive 45 and a second coupling arrangement 47 including a second pneumatic cylinder 46 are provided. The second pneumatic cylinder 46 is disposed on the bracket 22 and is movable together with the bracket 22 in the lateral direction Q. The second pneumatic cylinder 46 is assembled into a double acting cylinder.

As the piston of the second pneumatic cylinder 46 moves, the carriage 22 and the seat 20 can be moved relative to each other via the second coupling arrangement 47. According to this embodiment, the second pneumatic cylinder 46 is configured in parallel with the first pneumatic cylinder 31 such that the piston of the second pneumatic cylinder 46 is longitudinally movable in the cylinder housing. The piston of the second pneumatic cylinder 46 is connected to the piston rod 48 of the second pneumatic cylinder 46, which is protruded from the cylinder housing and its free end is connected to the shutter member 49. The shutter member 49 and the piston rod 48 are not movable relative to each other in the longitudinal direction L. The gate member 49 and the piston rod 48 are movable together, and in the exemplary embodiment, there is only one degree of freedom in the longitudinal direction L.

The shutter member 49 is guided in the longitudinal direction L via the two guide rails 50 extending in parallel with each other in the longitudinal direction L. Each of the two rails 50 together with the shutter member 49 can form a wear bearing, and according to this embodiment, a cross roller bearing (Fig. 5 and 6). The guide rail 50 is fastened to the bracket 22. As a result, the shutter member 49 can slide in the longitudinal direction L with respect to the bracket 22 by appropriately applying pressure to the second pneumatic cylinder 46.

The slotted gate 51 is disposed in the slotted gate member 49, which is eliminated by the two gate surfaces 52 that are parallel to each other. The two gate surfaces 52 may be formed by the groove side flank of the grooves in the gate member 49, or as opposed to the exemplary embodiment illustrated herein, with opposing sidewalls extending through the slits 53 of the shutter member 49. The slotted gate 51 or the two gate surfaces 52 define a gate path in which the shutter member 54 and the shutter member 49 are movable relative to each other. In the exemplary embodiment, the gate path is linearly parallel to the two gate surfaces 52 or parallel to the slot gates 51. The gate path is inclined with respect to the longitudinal direction L by an inclination angle α (Figs. 5 and 6). According to this embodiment, the inclination angle α is significantly less than 45°, and at most 30° or at most 20° is preferred. In this exemplary embodiment, the tilt angle a is equal to 10°.

The shutter member 54 is fixedly coupled to the seat body 20. According to this embodiment, the shutter member has a latch that extends away from the base 20 in the height direction H. To reduce wear and friction, the sleeve 56 can be coaxially disposed with respect to the pin 55 in a section of the latch 55 that extends through or into the slotted gate 51. In the exemplary embodiment, the sleeve 56 is configured to rotate about the axis of the pin 55. The outer diameter of the sleeve 56 is slightly smaller than the distance of the two gate surfaces 52 whereby the sleeve 56 is disposed in the slotted gate 51 with minimal possible clearance and is in contact with only one gate surface 52, respectively.

Gate element 54 or pin 55 extends through passage opening 57 of bracket 22 (Figs. 5 and 6). The passage opening 57 is of sufficient size in the lateral direction Q that movement of the bracket 22 relative to the seat body 20 is not obstructed by the shutter member 54. The gate member 54 or the latch 55 together with the passage opening 57 can define the two maximum positions of the movement of the carriage 22 relative to the seat body 20, which can be said to be the limit of motion of the stop. The passage opening 57 can be assembled in the form of elongated holes extending, for example, in the lateral direction Q.

If pressure is applied to one of the two working chambers of the double acting second pneumatic cylinder 46 of the linear actuator 56, the piston rod 48 moves into or out of the cylinder housing, and the shutter member 49 is in the longitudinal direction together with the piston rod 48. Moving relative to the carriage 22. As a result, the shutter member 49 is supported by the shutter member 54 disposed on the seat body 20 so as to be fixed at least in the longitudinal direction L and the lateral direction Q. The moving direction of the relative movement of the shutter member 49 and the shutter member 54 is defined by a gate path which is inclined with respect to the longitudinal direction L at an inclination angle α (in a plane formed by the longitudinal direction L and the lateral direction Q). The shutter member 49 is not movable laterally Q with respect to the bracket 22. The piston stroke of the second pneumatic cylinder 46 is simplified by the second coupling arrangement 47 into a linear motion of the carriage 22 relative to the seat 20. Due to this movement of the carriage 22 in the lateral direction Q along the seat body 20, it is possible, for example, to move the tailstock arm 16 toward and away from a workpiece. The axis of extension of the centering tip 12 is parallel to the pivot axis S, and according to this embodiment, the lateral direction Q. As a result, it is possible to engage the centering tip 12 with a workpiece or to press it against or away from the workpiece via movement of the carriage 22.

Due to a small scale tilt angle a of, for example, 10 degrees, a sufficient force can be applied via the second pneumatic cylinder 46 to the tailstock arm 16, wherein the force can be used to move or push the tailstock arm 16 or support configuration 11 against the workpiece. . The second pneumatic cylinder 46 provides a force that can be used by the second coupling arrangement 47 to be converted into the support arrangement 11 or the centering tip 12 can push the workpiece in the lateral direction Q. Due to the conversion of this force and the simplification of the path of the second coupling arrangement 47, it is possible to avoid shock-like movements when applying pressure to a working chamber of the second pneumatic cylinder 46, and to achieve sufficient between the support arrangement 11 and the workpiece. pressure.

As shown in FIG. 1, the tailstock assembly 10 includes a cover that is secured to the bracket 22. The cover 60 covers the pivot drive 30 and the linear drive 45 and prevents the shavings falling from the workpiece from entering the area where the two components can move relative to each other.

The invention relates to a tool for supporting a machine (for example, a grinder) The tailstock device 10 of one of the workpieces. The tailstock assembly 10 includes a tailstock arm 16 that is supported for pivoting about a pivot S that has been disposed on its outer end 16a with a centering tip 12 oriented parallel to the pivot S. With the pivoting actuator 30 including the first pneumatic cylinder 31, the tailstock arm 16 is movable between the operating position A and the rest position R. The movement of the piston 32 of the first pneumatic cylinder 31 is transmitted to the tailstock arm 16 via the first coupling arrangement 35. When the tailstock arm 16 is in the operating position A, the first coupling arrangement 35 assumes a self-locking position, at which point the force feedback effect triggered by the torque that would force the tailstock arm 16 to exit the working position A and enter the idle position R would not be or Only the piston 32 of the first pneumatic cylinder 31 is reacted minimally.

11‧‧‧Support configuration

12‧‧‧ Centering tip

15‧‧‧Carrier configuration

16‧‧‧Tailstock arm

16a‧‧‧The outer end of the tailstock arm 16

20‧‧‧ body

22‧‧‧ bracket

23‧‧‧Guide configuration

24‧‧‧ Track Guides

28‧‧‧ shaft

29‧‧‧ pivot bearing body

30‧‧‧ pivot drive

31‧‧‧First air cylinder

32‧‧‧Piston of the first pneumatic cylinder

33‧‧‧ piston rod

35‧‧‧First coupling configuration

36‧‧‧Actuating element

37‧‧‧Connecting parts

38‧‧‧ pivot rod

39‧‧‧First hinge

40‧‧‧Second hinge

41‧‧‧Guide

A‧‧‧Working position

H‧‧‧ Height direction

L‧‧‧ portrait

Q‧‧‧ Landscape

S‧‧‧ pivot

Claims (15)

A tailstock device (10) for supporting and/or centering a workpiece, comprising: a carrier arrangement (15) configured to be connectable to a machine tool, disposed on the carrier arrangement (15) a tailstock arm (16) supported on an inner end (16b) for pivoting about a pivot (S) and at an outer end (16a) opposite the inner end (16b) Carrying a support arrangement (11), a pivoting drive (30) includes a first pneumatic cylinder (31) and a first coupling arrangement (35), in which case one of the first pneumatic cylinders (31) The piston (32) is movably coupled to the inner end (16b) of the tailstock arm (16) via the first coupling arrangement (35), wherein the tailstock arm (16) is Moving between a working position (A) and a rest position (R), and wherein, when the working position (A) of the tailstock arm is applied to the tailstock arm (16), The first coupling arrangement (35) reduces or eliminates a force feedback effect on the first pneumatic cylinder (31) when the pivot (S) is centered at a torque. The tailstock device of claim 1, wherein the first coupling arrangement (35) comprises a torque-resistant connection to the inner end (16b) and extending from the pivot (S) to a rod end a pivoting lever (38), wherein a connecting member (37) is rotatably coupled to the rod end by a first hinge (39) and rotatably coupled to the actuating member (36) by a second hinge (40) In this case, the actuating element (36) is connected to the piston (32) of the first pneumatic cylinder (31). The tailstock device of claim 2, wherein when the tailstock arm (16) is in the working position (A), the orientation of the connector (37) is substantially at right angles to a longitudinal direction (L) such that The actuating element (36) is movable. The tailstock device of claim 2 or 3, wherein When the tailstock arm (16) is in the working position (A), the orientation of the connector (37) is substantially at right angles to the actuating element (36). A tailstock device according to any one of claims 1 to 4, wherein the connector (37) is oriented substantially parallel to the tailstock when the tailstock arm (16) is in the working position (A) Arm (16). The tailstock device of any one of claims 1 to 5, wherein the actuating element (36) is configured to slide along a longitudinal direction (L). A tailstock device according to any one of claims 1 to 6, wherein the pivoting drive (30) is used to force the tailstock arm (16) against the stop when in the working position (A) (42). A tailstock device according to any one of claims 1 to 7, wherein the carrier arrangement (15) comprises a body (20) arranged to be coupled to the machine tool, wherein a bracket (22) It is configured to slide on the seat body (20). The tailstock device of claim 8, wherein the tailstock arm (16) and the pivoting driver (30) are disposed on the bracket (22). The tailstock device of claim 8 or 9, wherein a linear actuator (45) is provided, the linear actuator comprising a second pneumatic cylinder (46) and a second coupling configuration (47), and The bracket (22) is slidable and/or positionable relative to the seat body (20). The tailstock device of claim 10, wherein the second coupling arrangement (47) includes a gate member (49) having a slotted gate (51) defining a gate path on the gate path A shutter member (49) movable relative to the shutter member (49) is disposed. The tailstock device of claim 10 or 11, wherein The second pneumatic cylinder (46) includes a piston movable in a longitudinal direction (L), and the bracket (22) is movable in a lateral direction (Q) which is oriented in the longitudinal direction (L) Right angle. The tailstock device of claim 11 and 12, wherein the gate path extends obliquely to the longitudinal direction (L) and the lateral direction (Q). The tailstock device of claim 13, wherein the gate path has an oblique angle (α) with the longitudinal direction (L), the angle being less than 45° or at most 30° or at most 20°. The tailstock device of any one of claims 10 to 14, wherein the second pneumatic cylinder (45) is disposed on the bracket (22).